US5792020A - Supporting structure of a ring gear supporting member in planetary gear device - Google Patents

Supporting structure of a ring gear supporting member in planetary gear device Download PDF

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Publication number
US5792020A
US5792020A US08/805,998 US80599897A US5792020A US 5792020 A US5792020 A US 5792020A US 80599897 A US80599897 A US 80599897A US 5792020 A US5792020 A US 5792020A
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US
United States
Prior art keywords
ring gear
thrust bearing
shaft portion
supporting member
planetary carrier
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Fee Related
Application number
US08/805,998
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English (en)
Inventor
Kimihiko Kikuchi
Takashi Hotta
Hisami Miyazaki
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Honda Motor Co Ltd
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Honda Motor Co Ltd
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Publication date
Application filed by Honda Motor Co Ltd filed Critical Honda Motor Co Ltd
Priority to US08/805,998 priority Critical patent/US5792020A/en
Application granted granted Critical
Publication of US5792020A publication Critical patent/US5792020A/en
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Definitions

  • the present invention relates to a supporting structure of a ring gear supporting member in a planetary gear device, including: a center shaft; a planetary carrier relatively rotatably fitted on an outer periphery of the center shaft through a shaft portion; an output member attached to the shaft portion; a ring gear supporting member having an inner periphery which is relatively rotatably fitted on said shaft portion and an outer periphery which supports a ring gear; and a first thrust bearing and a second thrust bearing for supporting opposite sides of the ring gear supporting member.
  • FIG. 4 shows the above-described conventional supporting structure.
  • the planetary gear device provided in an automatic speed change transmission of an automobile is provided with a sleeve 02 relatively rotatably fitted on an outer periphery of a main shaft 01.
  • a planetary carrier 03 is relatively rotatably supported on an outer periphery of the sleeve 02.
  • a shaft portion 04 1 of an output gear 04 for transmitting a driving force to a counter shaft (not shown) is fitted and spline-connected to an outer periphery of a shaft portion 03 1 formed integrally with the planetary carrier 03.
  • the output gear 04 is supported on a casing 05 of the transmission through a taper roller bearing 06.
  • a disk-like ring gear supporting member 07 provided with a ring gear (not shown) in an outer periphery thereof has one side supported by a first thrust bearing 08 disposed between it and one side of the planetary carrier 03, and the other side supported by a second thrust bearing 09 disposed between it and an end 04 2 of the shaft portion 04 1 of the output gear 04.
  • the ring gear supporting member 07 is supported rotatably relative to the planetary carrier 03 and the output gear 04.
  • the above-described conventional supporting structure has a problem in that vibrations of the ring gear supporting member 07 are directly transmitted to the output gear 04 through the second thrust bearing 09, which vibrations lead to a source of noises. There is a further problem in that since the planetary carrier 03, the ring gear supporting member 07, the first thrust bearing 08 and the second thrust bearing 09 cannot be preassembled as a unit, the mounting of those elements in the planetary gear device is difficult.
  • the present invention has been made in view of the aforementioned circumstances. It is an object of the present invention to provide a supporting structure of a ring gear supporting member in planetary gear device which can overcome the aforementioned problems.
  • a planetary gear device comprising a center shaft, a planetary carrier relatively rotatably fitted on an outer periphery of the center shaft through a shaft portion, an output member attached to the shaft portion, a ring gear supporting member having an inner periphery which is relatively rotatably fitted on said shaft portion and an outer periphery which supports a ring gear, and a first thrust bearing and a second thrust bearing for supporting opposite sides of the ring gear supporting member, wherein the first thrust bearing is interposed between one side of the ring gear supporting member and one side of the planetary carrier, and the second thrust bearing is interposed between the other side of the ring gear supporting member and the shaft portion.
  • the first thrust bearing is disposed between one side of the ring gear supporting member and one side of the planetary carrier
  • the second thrust bearing is disposed between the other side of the ring gear supporting member and the shaft portion, whereby vibrations of the ring gear supporting member are not directly transmitted to an output member through the second thrust bearing thereby overcoming the problems of generation and transmission of noises.
  • the first thrust bearing, the ring gear supporting member and the second thrust bearing can be integrally mounted and assembled on the shaft portion of the planetary carrier, the mounting of these elements is improved.
  • the locating precision between the planetary carrier and the output member is not affected by the precision of the dimensions of the first thrust bearing, the ring gear supporting member and the second thrust bearing, the quality control of the dimensions of those members is facilitated.
  • FIG. 1 is a longitudinal sectional view of a planetary gear device according to a first embodiment of the present invention
  • FIG. 2 is a view corresponding to FIG. 1 according to a second embodiment of the present invention.
  • FIG. 3 is an enlarged sectional view taken on line 3--3 of FIG. 2;
  • FIG. 4 is a longitudinal sectional view of a conventional planetary gear device.
  • a double-pinion type planetary gear device P provided in an automatic speed change transmission of an automobile is provided with a planetary carrier 3 supported on an outer periphery of a main shaft 1 with a sleeve 2 interposed therebetween.
  • a planetary carrier 3 On the planetary carrier 3 are supported a plurality of inner planetary gears 5i meshed with a sun gear 4 spline-connected to the outer periphery of the sleeve 2 and a plurality of outer planetary gears So meshed with planetary gears 5i and a ring gear 6.
  • An inner periphery of a disk-like ring gear supporting member 7 is relatively rotatably fitted on an outer periphery of a shaft portion 3, formed integrally with the planetary carrier 3, and the ring gear 6 is fixedly mounted on the outer periphery of the ring gear supporting member 7.
  • An output gear 10 as an output member supported on a casing 8 of the automatic speed change transmission through a ball bearing 9 is integrally provided with a shaft portion 10 1 spline-connected at 11 to the outer periphery of the shaft portion 3 1 of the planetary carrier 3.
  • An outer race 9 1 of the ball bearing 9 is secured to the casing 8 by means of a pair of circlips 17 and 18, and the output gear 10 is secured to an inner race 9 2 of the ball bearing 9 by means of a nut 12 threaded into the outer periphery of the end of the shaft portion 101.
  • a first thrust bearing 13 is interposed between the right side of the ring gear supporting member 7 and the left side of the planetary carrier 3.
  • a second thrust bearing 16 is interposed between a washer 15, secured by a circlip 14 to the shaft portion 3 1 of the planetary carrier 3, and the left side of the ring gear supporting member 7.
  • An end of the shaft portion 10 1 of the output gear 10 is abutted against and positioned at a shoulder 3 2 formed adjacent to but with a spacing from the left side of the circlip 14 on the outer periphery of the shaft portion 3 1 of the planetary carrier 3.
  • the thrust force exerting on the output gear 10 during the operation of the planetary gear device P is received by the casing 8 through the ball bearing 9.
  • the leftward thrust force exerted on the planetary carrier 3 and the leftward thrust force transmitted from the ring gear supporting member 7 to the planetary carrier 3 are received by the casing 8 through the output gear 10 and the ball bearing 9.
  • the vibrations of the ring gear supporting member 7 are transmitted to the planetary carrier 3 through the first thrust bearing 13 and the second thrust bearing 16.
  • the vibrations transmitted from the ring gear supporting member 7 to a counter shaft (not shown) through the output gear 10 are moderated to reduce noises.
  • the first thrust bearing 13, the ring gear supporting member 7, the second thrust bearing 16, the washer 15 and the circlip 14 can be mounted in advance on the shaft portion 3 1 of the planetary carrier 3 and assembled. Therefore, the mounting ability can be considerably improved as compared with the case where the planetary carrier 3, the first thrust bearing 13, the ring gear supporting member 7 and the second thrust bearing 16, etc. are separately mounted.
  • the precision required in locating one side B of the planetary carrier 3 relative to a reference surface A of the casing 8 merely depends on the dimensional precision of the ball bearing 9, the output gear 10 and the planetary carrier 3 but does not depend on the dimensional precision of the first thrust bearing 13, the ring gear supporting member 7 and the second thrust bearing 16, as in the prior art construction shown in FIG. 4. Therefore, the quality control of dimensions is easy as compared with the prior art shown in FIG. 4.
  • the positioning of the ring gear supporting member 7 supported on the planetary carrier 3 can be easily performed merely by adjusting the thickness of the washer 15.
  • the second thrust bearing 16 in the second embodiment is not provided with a bearing race on the left side (on the circlip 14 side), but rather the washer 15 functions as the bearing race.
  • Spline grooves 3 3 formed in the outer periphery of the shaft portion 3 1 of the planetary carrier 3 to fix the shaft portion 10 1 of the output gear 10 slope radially outwardly on the right end side (on the second thrust bearing 16 side).
  • Four anti-swivel protrusions 15 1 extend inwardly at intervals of 90° from the inner periphery of the washer 15.
  • the anti-swivel protrusions 15 1 are fitted in the spline grooves 3 3 which slope radially outwardly whereby the anti-swivel function can be applied to the washer 15 without using a separate member.
  • the reference character 14 1 designates an outer peripheral edge of the circlip 14
  • the reference character 14 2 designates an inner peripheral edge of the circlip 14, which is broken-away in the drawing to illustrate the protrusion 15 1 .
  • Other components and constructions of the second embodiment are the same as those of the afore-described first embodiment, whereby their description will not be repeated here, but the second embodiment can achieve the same operations and effects as those of the first embodiment.
  • the double-pinion type planetary gear device P having the inner planetary gears 5i meshed with the sun gear 4 and the outer planetary gears 5o meshed with the ring gear 6 has been illustrated, it is to be noted that the present invention also can be applied to a single pinion type planetary gear device P having planetary gears which are simultaneously meshed with the sun gear 4 and the ring gear 6.
  • the number of the anti-swivel protrusions 15 1 formed on the washer 25 is not limited to four but can be suitably changed.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Details Of Gearings (AREA)
  • Structure Of Transmissions (AREA)
  • Retarders (AREA)
US08/805,998 1994-03-01 1997-02-24 Supporting structure of a ring gear supporting member in planetary gear device Expired - Fee Related US5792020A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US08/805,998 US5792020A (en) 1994-03-01 1997-02-24 Supporting structure of a ring gear supporting member in planetary gear device

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP6031594A JPH07238998A (ja) 1994-03-01 1994-03-01 遊星歯車装置におけるリングギヤ支持部材の支持構造
JP6-031594 1994-03-01
US39561295A 1995-02-28 1995-02-28
US08/805,998 US5792020A (en) 1994-03-01 1997-02-24 Supporting structure of a ring gear supporting member in planetary gear device

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US39561295A Continuation 1994-03-01 1995-02-28

Publications (1)

Publication Number Publication Date
US5792020A true US5792020A (en) 1998-08-11

Family

ID=12335528

Family Applications (1)

Application Number Title Priority Date Filing Date
US08/805,998 Expired - Fee Related US5792020A (en) 1994-03-01 1997-02-24 Supporting structure of a ring gear supporting member in planetary gear device

Country Status (7)

Country Link
US (1) US5792020A (ja)
EP (1) EP0674123B1 (ja)
JP (1) JPH07238998A (ja)
KR (1) KR950033179A (ja)
CA (1) CA2143546C (ja)
DE (1) DE69521227T2 (ja)
TW (1) TW286301B (ja)

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5916056A (en) * 1997-02-26 1999-06-29 Jatco Corporation Splined ring gear having a thicker radial portion at one axial portion of the ring gear
US6033335A (en) * 1997-10-30 2000-03-07 Honda Giken Kogyo Kabushiki Kaisha Planetary gear mechanism
DE102007021194A1 (de) * 2007-05-05 2008-11-06 Zf Friedrichshafen Ag Bauteil mit Innen- und Außenverzahnung
US20130059684A1 (en) * 2010-05-26 2013-03-07 Toyota Jidosha Kabushiki Kaisha Belt type continuously variable transmission
US8714888B2 (en) 2010-10-25 2014-05-06 Black & Decker Inc. Power tool transmission
US9022196B2 (en) 2012-03-27 2015-05-05 Schaeffler Technologies AG & Co. KG Clutch assembly with a tab rivet connection and method thereof
US9481080B2 (en) 2011-07-29 2016-11-01 Black & Decker Inc. Multispeed power tool
US11059160B2 (en) 2011-07-29 2021-07-13 Black & Decker Inc. Multispeed power tool

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3243090A1 (de) * 1982-11-22 1984-05-24 Gesellschaft für Biotechnologische Forschung mbH (GBF), 3300 Braunschweig Verfahren zur herstellung von (+)-(alpha)-terpineol durch mikrobiologische umwandlung von limonen
JP2003106339A (ja) * 2001-09-28 2003-04-09 Jatco Ltd 自動変速機におけるスプライン部の結合構造
DE102008043279A1 (de) * 2008-10-29 2010-05-06 Zf Friedrichshafen Ag Getriebevorrichtung mit wenigstens einem schrägverzahnten Planetenradsatz
US10941849B2 (en) * 2017-08-03 2021-03-09 General Electric Company Gear assembly damper arrangement

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4270412A (en) * 1978-02-08 1981-06-02 Saab-Scania Aktiebolag Hub gear for wheeled vehicles
US4387607A (en) * 1979-08-30 1983-06-14 Aisin Warner Kabushiki Kaisha Overdrive unit in automatic transmissions
US4656890A (en) * 1985-12-19 1987-04-14 Dresser Industries, Inc. Coupling for a planetary ring gear
US4730517A (en) * 1985-08-27 1988-03-15 Toyota Jidosha Kabushiki Kaisha Helical planetary gear assembly
US4914978A (en) * 1986-12-09 1990-04-10 Aisin-Warner Kabushiki Kaisha Automatic transmission
US4994007A (en) * 1986-12-09 1991-02-19 Aisin Aw Co., Ltd. Counter gear supporting device for an automatic transmission
EP0453118A1 (en) * 1990-04-16 1991-10-23 Eaton Corporation Improved transmission thrust washer and locking means therefor
US5295925A (en) * 1991-11-22 1994-03-22 Harmonic Drive Systems, Inc. Planetary gear transmission
US5480361A (en) * 1993-01-27 1996-01-02 Nissan Motor Co., Ltd. Change direction planetary gearing for continuously variable transmission
US5643126A (en) * 1995-03-31 1997-07-01 Honda Giken Kogyo Kabushiki Kaisha Lubricating oil supply structure in planetary gear mechanism

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5142861A (ja) * 1974-10-09 1976-04-12 Aisin Seiki Juseihagurumasochino junkatsusochi
JPH0650127B2 (ja) * 1984-01-24 1994-06-29 アイシン・エィ・ダブリュ株式会社 動力伝達装置
JPH0814302B2 (ja) * 1988-08-04 1996-02-14 アイシン・エィ・ダブリュ株式会社 自動変速機におけるプラネタリリングギヤの支持装置

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4270412A (en) * 1978-02-08 1981-06-02 Saab-Scania Aktiebolag Hub gear for wheeled vehicles
US4387607A (en) * 1979-08-30 1983-06-14 Aisin Warner Kabushiki Kaisha Overdrive unit in automatic transmissions
US4730517A (en) * 1985-08-27 1988-03-15 Toyota Jidosha Kabushiki Kaisha Helical planetary gear assembly
US4656890A (en) * 1985-12-19 1987-04-14 Dresser Industries, Inc. Coupling for a planetary ring gear
US4914978A (en) * 1986-12-09 1990-04-10 Aisin-Warner Kabushiki Kaisha Automatic transmission
US4994007A (en) * 1986-12-09 1991-02-19 Aisin Aw Co., Ltd. Counter gear supporting device for an automatic transmission
US5026337A (en) * 1986-12-09 1991-06-25 Aisin Aw Co., Ltd. Supporting device of a planetary ring gear for an automatic transmission
EP0453118A1 (en) * 1990-04-16 1991-10-23 Eaton Corporation Improved transmission thrust washer and locking means therefor
US5295925A (en) * 1991-11-22 1994-03-22 Harmonic Drive Systems, Inc. Planetary gear transmission
US5480361A (en) * 1993-01-27 1996-01-02 Nissan Motor Co., Ltd. Change direction planetary gearing for continuously variable transmission
US5643126A (en) * 1995-03-31 1997-07-01 Honda Giken Kogyo Kabushiki Kaisha Lubricating oil supply structure in planetary gear mechanism

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
Abstract of JP 1087944, published Apr. 1989 (English translation). *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5916056A (en) * 1997-02-26 1999-06-29 Jatco Corporation Splined ring gear having a thicker radial portion at one axial portion of the ring gear
US6033335A (en) * 1997-10-30 2000-03-07 Honda Giken Kogyo Kabushiki Kaisha Planetary gear mechanism
DE102007021194A1 (de) * 2007-05-05 2008-11-06 Zf Friedrichshafen Ag Bauteil mit Innen- und Außenverzahnung
US20100137096A1 (en) * 2007-05-05 2010-06-03 Zf Friedrichshafen Ag Component having inner and outer gearing
US8888617B2 (en) * 2010-05-26 2014-11-18 Toyota Jidosha Kabushiki Kaisha Belt type continuously variable transmission
US20130059684A1 (en) * 2010-05-26 2013-03-07 Toyota Jidosha Kabushiki Kaisha Belt type continuously variable transmission
US8714888B2 (en) 2010-10-25 2014-05-06 Black & Decker Inc. Power tool transmission
US9481080B2 (en) 2011-07-29 2016-11-01 Black & Decker Inc. Multispeed power tool
US10464201B2 (en) 2011-07-29 2019-11-05 Black & Decker Inc. Multispeed power tool
US11059160B2 (en) 2011-07-29 2021-07-13 Black & Decker Inc. Multispeed power tool
US11491632B2 (en) 2011-07-29 2022-11-08 Black & Decker Inc. Multispeed power tool
US12011814B2 (en) 2011-07-29 2024-06-18 Black & Decker Inc. Multispeed power tool
US9022196B2 (en) 2012-03-27 2015-05-05 Schaeffler Technologies AG & Co. KG Clutch assembly with a tab rivet connection and method thereof

Also Published As

Publication number Publication date
KR950033179A (ko) 1995-12-22
EP0674123A2 (en) 1995-09-27
DE69521227D1 (de) 2001-07-19
EP0674123B1 (en) 2001-06-13
TW286301B (ja) 1996-09-21
CA2143546A1 (en) 1995-09-02
CA2143546C (en) 1998-12-29
EP0674123A3 (en) 1997-08-20
JPH07238998A (ja) 1995-09-12
DE69521227T2 (de) 2001-09-20

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